CN109642570A - Screw compressor - Google Patents
Screw compressor Download PDFInfo
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- CN109642570A CN109642570A CN201780040848.9A CN201780040848A CN109642570A CN 109642570 A CN109642570 A CN 109642570A CN 201780040848 A CN201780040848 A CN 201780040848A CN 109642570 A CN109642570 A CN 109642570A
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- counterweight
- crankshaft
- oil
- screw compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The present invention inhibits the oil to discharge chambe excess supply, and reduces counterweight to the churn loss of oil, realizes that performance improves.Screw compressor has: the crankshaft with cam pin portion；Swirling scroll has the convolution lug boss engaged with cam pin portion via convolution bearing；Fixed eddy plate；Frame；Accommodate these closed container；And in order to which the end of the oil supply of the oil storage tank in the closed container to cam pin portion to be formed in the oil supplying hole of crankshaft.In addition, having: counterweight is configured in said frame, and is fixed on crankshaft；The clearance portion of counterweight is penetrated through in the axial direction；Set on the first seal member than the clearance portion between the counterweight and swirling scroll of outside diameter；And set on the second seal member than above-mentioned clearance portion between the counterweight and frame of outside diameter.
Description
Technical field
The present invention relates to screw compressor, it is especially suitable for the screw compressor as use in refrigeration system.
Background technique
As the existing screw compressor for air conditioner etc., has and be for example recorded in Japanese Unexamined Patent Publication 2011-226447
The screw compressor of number bulletin (patent document 1).
As documented by the patent document 1, screw compressor is in the pin portion of the axle center bias relative to crankshaft (axis)
(crank portion) has swirling scroll via the sliding bearing engaging for being known as convolution bearing.Thereby, it is possible to so that above-mentioned swirling scroll is circled round
Movement, the fluids such as compression refrigerant still with the circumnutation of above-mentioned swirling scroll, generate centrifugal force in above-mentioned crankshaft.
It is uneven because of caused by the centrifugal force in order to offset, there is counterweight in crankshaft installed.Counterweight is generally more installed on
It, more being capable of lightweight axially closer to the position of swirling scroll.Therefore, counterweight is accommodated in the frame stored to swirling scroll
The frame of lightweight inside to(for) counterweight is effective.
In the patent document 1, frame is split, configures counterweight inside it, it is close as a result, to act on convolution whirlpool
The position of the centrifugal force of each of disk and counterweight, realizes the lightweight of counterweight.
On the other hand, screw compressor to above-mentioned rotary shaft in order to hold, support the base bearing isometric bearing portion, anti-of above-mentioned crankshaft
The only anti-rotation mechanism (euclidean Ring) and above-mentioned swirling scroll and the sliding part of fixed eddy plate etc. of the rotation of above-mentioned swirling scroll
Each sliding part is for oil supply, generally, the oil supply mechanism portion being made of oil feed pump etc. is arranged in the lower end of above-mentioned crankshaft, above-mentioned
The inside of crankshaft is equipped with the oil supplying hole penetrated through in the axial direction.
By above-mentioned oil supply mechanism portion supply come oil via above-mentioned oil supplying hole from set on above-mentioned crankshaft upper end above-mentioned pin
The end in portion is discharged, and each sliding part such as supply to above-mentioned rotary shaft is held, above-mentioned whirlpool disk sliding part.
Existing technical literature
Patent document
Patent document 1: 2011-No. 226447 bulletins of Japanese Unexamined Patent Publication
Summary of the invention
Problems to be solved by the invention
In the screw compressor of use in refrigeration system, refrigerant is sucked from suction inlet, by by swirling scroll and fixed eddy plate
The volume of the discharge chambe of formation changes to compress above-mentioned refrigerant, therefore, when to the oil of above-mentioned discharge chambe excess supply, largely
Oil be present in discharge chambe, accordingly, because heating of the oil of the smaller volume of discharge chambe that can be used for compressing, high temperature to refrigerant
Deng so becoming the reason of compressor performance reduces.
In addition, when the oil of the space excess supply rotated to above-mentioned counterweight, not due to counterweight outstanding radially
Stirring of the balance portion to oil, generates churn loss, also becomes the reason of compressor performance reduces as a result,.
In above patent document 1, frame is divided into upper and lower part, stores counterweight, Er Qie in the lower portion
Seal member is set between the frame on above-mentioned top and the lug boss of swirling scroll, is thus separated into the pressure close to discharge pressure
Inside the first space and the outside as the pressure between discharge pressure and suction pressure second space.It limits as a result,
Above-mentioned second space from oil to the swirling scroll back side being connected to discharge chambe supply, not to above-mentioned discharge chambe excess supply
Oil, to inhibit the reduced performance of compressor.
But in above patent document 1, it is configured with above-mentioned counterweight in bent axial above-mentioned first space side, is not limited
Inflow of the liquefaction to the space configured with the counterweight, therefore, in the space full of a large amount of oil.Therefore, when above-mentioned counterweight rotates
When, the uneven portion of the counterweight is generated to the churn loss of oil, there are problems that compressor performance reduction.
It is an object of the invention to obtain a kind of screw compressor, it is able to suppress the oil to discharge chambe excess supply, and
And counterweight is reduced to the churn loss of oil, realize that performance improves.
Solution for solving the problem
In order to solve the above problems, the present invention is a kind of screw compressor, is had: being had relative to the inclined of axle center bias
The crankshaft in heart pin portion；Swirling scroll, platen have vortex and set on the vortex opposite side and with above-mentioned cam pin
The convolution lug boss that portion engages via convolution bearing；Fixation whirlpool with the vortex that the vortex with the swirling scroll engages
Disk；It fixes the fixed eddy plate and stores above-mentioned swirling scroll, and there is the frame for the base bearing for supporting above-mentioned crankshaft；For making
The driving portion of above-mentioned crankshaft rotation；Accommodate these closed container；And for the oil storage tank that will be set in the closed container
Oil supplies to the end in above-mentioned cam pin portion and is formed in the above-mentioned axial oil supplying hole of song, the feature of above-mentioned screw compressor
Be have: counterweight is configured in the said frame below above-mentioned swirling scroll, and is fixed on above-mentioned crankshaft, and be used for
Negative function is generated in the centrifugal force in above-mentioned cam pin portion and the direction of the centrifugal force of above-mentioned swirling scroll；In the axial direction in perforation
State the clearance portion of counterweight；Set on the first sealing than above-mentioned clearance portion between the above-mentioned counterweight and above-mentioned swirling scroll of outside diameter
Component；And set on the second seal member than above-mentioned clearance portion between the above-mentioned counterweight and said frame of outside diameter.
The effect of invention
According to the present invention it is possible to obtain following effect: a kind of screw compressor can be obtained, which can
Inhibit the oil to discharge chambe excess supply, and reduce counterweight to the churn loss of oil, realizes that performance improves.
Detailed description of the invention
Fig. 1 is the longitudinal section view for indicating the embodiment 1 of screw compressor of the invention.
Fig. 2 is the enlarged cross-sectional view near the frame of Fig. 1.
Fig. 3 is the figure for indicating the variation of embodiment 1 shown in FIG. 1, is comparable to the figure of Fig. 2.
Fig. 4 is crankshaft shown in Fig. 2 and the figure of counterweight from the end side in cam pin portion.
Fig. 5 is crankshaft shown in Fig. 2 and the figure of counterweight from thrust bearing side.
Fig. 6 is the figure for indicating the embodiment 2 of screw compressor of the invention, is comparable to the figure of Fig. 2.
Fig. 7 is crankshaft shown in fig. 6 and the figure of counterweight from the end side in cam pin portion.
Fig. 8 is crankshaft shown in fig. 6 and the figure of counterweight from thrust bearing side.
Specific embodiment
Hereinafter, being based on attached drawing, the specific embodiment of screw compressor of the invention is illustrated.In each figure, mark
The part of the same symbol indicates the same or similar part.
Embodiment 1
Illustrate the embodiment 1 of screw compressor of the invention using FIG. 1 to FIG. 5.Fig. 1 is to indicate scroll compression of the invention
The longitudinal section view of the embodiment 1 of machine, Fig. 2 are the enlarged cross-sectional views near the frame in Fig. 1, and Fig. 3 is to indicate implementation shown in FIG. 1
The figure of the variation of example 1, Fig. 4 are crankshaft shown in Fig. 2 and the figure of counterweight from the end side in cam pin portion, and Fig. 5 is from only
Observe the figure of crankshaft shown in Fig. 2 and counterweight in thrust bearing side.
Firstly, being illustrated using Fig. 1 to the overall structure of the screw compressor of the present embodiment 1.
Screw compressor 1 stores compression mechanical part 3, driving portion 4, rotation axle portion 5 and oil supply mechanism in closed container 2
Portion 6 etc. and constitute.
Compression mechanism section 3 with swirling scroll 7, fixed eddy plate 8, the frame 9 being fixed in above-mentioned closed container 2 and
Anti-rotation mechanisms 10 etc. are constituted for fundamental.
Above-mentioned swirling scroll 7 erects the convolution of the whirlpool disk shape of setting with platen 7a, in the face of a side side of platen 7a
Whirlpool disk vortex (whirlpool plate) 7b, it hangs down in the center in the face of the side opposite with above-mentioned swirling scroll vortex 7b of above-mentioned platen 7a
The convolution lug boss 7c directly being provided projectingly and the convolution bearing 7d being arranged in above-mentioned convolution lug boss 7c etc. are to want substantially
Element and constitute.As above-mentioned convolution bearing 7d, sliding bearing is used.
Above-mentioned fixed eddy plate 8 vertically erects the fixed eddy plate rotation of the whirlpool disk shape of setting with platen 8a, in platen 8a
Whirlpool body (whirlpool plate) 8b, it is set in the suction inlet 8c of the peripheral side of above-mentioned platen 8a setting and in the center side of above-mentioned platen 8a
Discharge opening 8d set etc. is constituted for fundamental.Keep fixed eddy plate vortex 8b opposed with above-mentioned swirling scroll vortex 7b,
It is engaged in a manner of forming discharge chambe 11, then the fixed eddy plate 8 is fixed on said frame 9 by bolt 33.
The said frame 9 being fixed in closed container 2 is tight with the fixed eddy plate for fastening above-mentioned fixed eddy plate 8 by bolt 33
Gu it is fundamental and structure that face 9a and storage, which are freely and rotatably supported gimbal axis bearing portion 9b of base bearing 13 of crankshaft 12 etc.,
At.
Above-mentioned anti-rotation mechanism 10 for make above-mentioned swirling scroll 7 relative to above-mentioned fixed eddy plate 8 not autobiography and returned
Rotation movement.The anti-rotation mechanism 10 is accommodated in said frame 9, and to be sticked in the platen of the frame 9 and above-mentioned swirling scroll 7
The mode of the vortex opposite side of 7a is constituted.
Above-mentioned driving portion 4 is constituted, above-mentioned motor with having the motor 16 of stator 14 and rotor 15 for fundamental
Turning effort by driving from the electrical input of power supply (not shown) via electric terminal 17, is applied to crankshaft by 16
12。
It rotates axle portion 5 and is fixed on the ratio in above-mentioned closed container 2 with above-mentioned crankshaft 12, above-mentioned base bearing 13, by plug welding
Above-mentioned motor 16 is fixed on the pair frame by the sub-frame 18 of lower part (side opposite with compression mechanical part 3), by bolt 34
The supplementary bearing shell 20 of frame 18, the supplementary bearing 19 in the supplementary bearing shell 20 and it is configured at 7 lower section of above-mentioned swirling scroll
Said frame 9 in and the counterweight 21 that is fixed on above-mentioned crankshaft 12 is equal is fundamental and constitutes.Above-mentioned sub-frame 18 and upper
It states supplementary bearing shell 20 and is also configured to Construction integration.
Above-mentioned crankshaft 12 is with main shaft part 12a, countershaft portion 12b, cam pin portion 12c, flange part 12d, oil supplying hole (through hole)
12e etc. is constituted for fundamental.Above-mentioned main shaft part 12a is freely and rotatably supported by above-mentioned base bearing 13, above-mentioned countershaft portion 12b
It is freely and rotatably supported by above-mentioned supplementary bearing 19.In addition, the above-mentioned song between above-mentioned main shaft part 12a and above-mentioned countershaft portion 12b
Axis 12 is fixed with the above-mentioned rotor 15 of above-mentioned motor 16.
Above-mentioned cam pin portion 12c is via the above-mentioned convolution bearing 7d and above-mentioned convolution whirlpool being set in above-mentioned convolution lug boss 7c
Disk 7 engages.In addition, above-mentioned flange part 12d is located at the lower part (upper end above-mentioned main shaft part 12a) in the above-mentioned portion 12c, cam pin portion, constitute
For the diameter bigger than above-mentioned main shaft part 12a and above-mentioned cam pin portion 12c.
Above-mentioned oil supply mechanism portion 6 engages with the lower end of above-mentioned crankshaft 12, using the rotation of the crankshaft 12 under closed container 2
The up oil suction of oil storage tank 22 in portion supplies oil extremely via the above-mentioned oil supplying hole 12e formed in the axial direction in above-mentioned crankshaft 12
Each sliding part of compressor.As the fuel system in above-mentioned oil supply mechanism portion 6, centrifugal pump, positive displacement pump are generally used.
In screw compressor 1 configured as described, when rotating above-mentioned crankshaft 12 by motor 16, above-mentioned time
7 circumnutation of vortex disk subtracts its volume by the discharge chambe 11 that swirling scroll vortex 7b and fixed eddy plate vortex 8b are formed
It is few, carry out compressed action.
In the working fluid (refrigerant) that the refrigerating cycle of air conditioner etc. flows via the sucking for being set to above-mentioned closed container 2
Pipe 23 is imported into the above-mentioned suction inlet 8c for being formed in fixed eddy plate 8 outside closed container 2, is then drawn into above-mentioned discharge chambe 11.
The above-mentioned working fluid of discharge chambe 11 is drawn by the compression travel based on above-mentioned compressed action, is spat from above-mentioned discharge opening 8d
Out to the discharge space 35 being formed in above-mentioned closed container 2, then by being set to above-mentioned fixed eddy plate 8 and said frame 9
The axial access 36 of periphery, flows to 37 side of motor room of 9 lower part of frame, then, from the discharge pipe for being set to closed container 2
24 by the above-mentioned refrigerating cycle to outside closed container 2 that spues.
In addition, in Fig. 1,9d be in order to be discharged to the oil that above-mentioned convolution bearing 7d, above-mentioned base bearing 13 are lubricated and
It is formed in the oil extraction path of said frame 9,38 be under the oil guidance to closed container 2 for will be discharged from above-mentioned oil extraction path 9d
The oil exit pipe of the above-mentioned oil storage tank 22 in portion.From the above-mentioned oil supplying hole 12e of above-mentioned crankshaft 12 is formed in via being formed in above-mentioned crankshaft
12 cross-drilled hole 9e, 9f in above-mentioned base bearing 13, above-mentioned supplementary bearing 19 for oil supply.
Next, Fig. 2 used as the enlarged cross-sectional view near said frame 9, to the major part of the present embodiment
Structure is described in detail.
The master of above-mentioned swirling scroll 7, above-mentioned anti-rotation mechanism 10, above-mentioned crankshaft 12 is accommodated in the inside of said frame 9
Axle portion 12a, cam pin portion 12c and above-mentioned flange part 12d, above-mentioned counterweight 21 etc..
Above-mentioned counterweight 21 is made of ring portion 21a and imbalance portion 21b, by the methods of indentation, hot jacket in above-mentioned ring portion 21a
It is fixed on above-mentioned crankshaft 12.The imbalance that above-mentioned imbalance portion 21b is generated in counteracting by the circumnutation of above-mentioned swirling scroll 7
Side set up.In addition, above-mentioned crankshaft 12 is inserted into from the lower end side of above-mentioned counterweight 21, above-mentioned counterweight 21 is connected to above-mentioned flange
The lower end surface of portion 12d and be fixed on above-mentioned crankshaft 12 in the axial direction.
The groove 21e for accommodating the first seal member 25 is formed in the upper surface of the ring portion 21a of above-mentioned counterweight 21.Above-mentioned
One seal member 25 is set between the sliding surface 7e of the convolution lower end lug boss 7c of above-mentioned counterweight 21 and above-mentioned swirling scroll 7, and
It slides with swirling scroll 7, will be sealed between above-mentioned swirling scroll 7 and above-mentioned ring portion 21a on one side on one side.
On the other hand, thrust bearing is installed in the end face 9c of the said frame 9 opposed with the ring portion 21a of above-mentioned counterweight 21
26.The thrust bearing 26 supports the ring portion 21a of above-mentioned counterweight 21, and is configured to, and support acts on above-mentioned song via the counterweight 21
The axial load of axis 12.Although acting on the reaction force from above-mentioned thrust bearing 26, the counterweight 21 to above-mentioned counterweight 21
It is connected to the lower surface (stage portion) of above-mentioned flange part 12d and fixes, therefore will not be moved in the axial direction relative to crankshaft 12.
The above-mentioned thrust bearing 26 also ring portion 21a with one side and counterweight 21 is slided, on one side by the ring portion 21a of counterweight 21 with
The function of sealing between end face 9c frame 9 and that counterweight is opposed, has both the function of (the second seal member) as a seal part.
In order to make above-mentioned thrust bearing 26 that also there is sufficient function as a seal part, above-mentioned thrust shaft preferably is constituted with resin bearing
Hold 26.
In addition, in the case where cannot get sufficient leakproofness by above-mentioned thrust bearing 26, as shown in figure 3, can also be with
It is configured to, second seal member same as above-mentioned first seal member 25 is being set by outside diameter than above-mentioned thrust bearing 26
31.That is, Fig. 3 is the variation for indicating embodiment 1 shown in FIG. 1, with Fig. 2's the difference lies in that in the ring portion 21a with counterweight 21
The end face 9c of opposed frame 9 is also equipped with above-mentioned second seal member 31 other than above-mentioned thrust bearing 26.That is, be configured to,
Above-mentioned thrust bearing 26 is disposed in part corresponding with the inner circumferential side of above-mentioned ring portion 21a, is leaning on outside diameter than the thrust bearing 26
And the end face 9c of the frame 9 opposed with above-mentioned ring portion 21a forms groove 21f, and above-mentioned second seal member is arranged in groove 21f
31。
With this configuration, the material of above-mentioned thrust bearing 26 is not limited to the bearing of the good resin of leakproofness, can also
To use the bearing part etc. with back metal.Other structures are identical as structure shown in Fig. 2.
As described above, passing through the first seal member 25 shown in Fig. 2 and thrust bearing (the second seal member) 26, Huo Zhetong
The first seal member 25 shown in Fig. 3 and the second seal member 31 are crossed, the space configured with counterweight 21 is divided into than above-mentioned ring
Space 29 and space, that is, back pressure chamber 28 than above-mentioned ring portion 21a in the outer part near the space, that is, crankshaft of portion 21a in the inner part.
By above-mentioned first seal member 25, above-mentioned second seal member, (thrust bearing 26, second seals above-mentioned back pressure chamber 28
Component 31), above-mentioned swirling scroll 7, above-mentioned fixed eddy plate 8, said frame 9 and above-mentioned counterweight 21 mark off.Above-mentioned crankshaft is attached
Near space 29 is by above-mentioned first seal member 25, above-mentioned second seal member (thrust bearing 26, the second seal member 31), above-mentioned
Crankshaft 12, above-mentioned swirling scroll 7, said frame 9 and above-mentioned counterweight 21 mark off.
Use Fig. 2, Fig. 4 of the crankshaft shown in Fig. 2 and counterweight and from thrust shaft from the end side in cam pin portion
The structure in space 29 near above-mentioned crankshaft is described in detail in the Fig. 5 for holding side observation.
As shown in Figure 4, Figure 5, it in the internal side diameter of the ring portion 21a of counterweight 21, is equipped at three to radially inner side in the circumferential
Claw (support portion) 21c outstanding, by claw 21c, counterweight 21 is fixed on crankshaft 12 by the methods of hot jacket, indentation.This
Outside, above-mentioned claw 21c is not limited at three, can also be more than circumferentially setting everywhere.
Inner peripheral surface 21d other than the above-mentioned claw 21c of above-mentioned counterweight 21 is formed as leaning on than the flange part 12d of above-mentioned crankshaft 12
Radial outside.By the above-mentioned inner peripheral surface 21d and above-mentioned claw 21c and above-mentioned crankshaft 12 and above-mentioned flange part of the counterweight 21
Outer peripheral surface forms the clearance portion (oily access) 32 of the interconnecting piece of perforation counterweight 21 and crankshaft 12 in the axial direction.
In addition, as shown in Fig. 2, the sliding surface 7e in the above-mentioned lower end convolution lug boss 7c of above-mentioned swirling scroll 7 is equipped with and divides
Branch path 30, the individual path 30 are used for above-mentioned first seal member 25 through the circumnutation of swirling scroll 7 radially
It is crosscutting, by the oil supply of the high pressure in space 29 near above-mentioned crankshaft to above-mentioned back pressure chamber 28.As the example of the individual path 30, energy
It is enough to be made of bag slot, slit.
In example shown in Fig. 2, by making space (first near above-mentioned crankshaft according to the circumnutation of above-mentioned swirling scroll 7
The space of 25 internal side diameter of seal member) 29 and above-mentioned back pressure chamber (space of 25 outside diameter of the first seal member) 28 intermittently connect
Logical slit constitutes above-mentioned individual path 30.The slit (individual path 30) with swirling scroll 7 circumnutation intermittently
Across above-mentioned first seal member 25, space near above-mentioned crankshaft is intermittently thus supplied to above-mentioned back pressure chamber 28 using pressure difference
The oil of 29 high pressure.
In addition, being configured in the case where constituting above-mentioned individual path 30 by bag slot, in the cunning of above-mentioned convolution lug boss 7c
Dynamic face 7e is formed in one or more bag of slot (hole), this bag of slot crosses over above-mentioned first seal member with the circumnutation of swirling scroll 7
25, it is moved between space 29 and above-mentioned back pressure chamber 28 near above-mentioned crankshaft.Thereby, it is possible to above-mentioned back pressure chamber 28 intermittently
Supply the oil of the high pressure in space 29 near above-mentioned crankshaft.
Oil due to the high pressure in space 29 near above-mentioned crankshaft is being sealed via above-mentioned fuel supply path 30 across above-mentioned first
It is depressurized when the supply of component 25 to above-mentioned back pressure chamber 28, therefore space 29 near the above-mentioned crankshaft of pressure ratio of above-mentioned back pressure chamber 28
Pressure is low.In addition, in order to adjust the pressure (back pressure) of above-mentioned back pressure chamber 28, above-mentioned fixed eddy plate 8 or said frame 9 be equipped with by
The pressure adjustmenting mechanism (not shown) of the compositions such as Back pressure control valve.Above-mentioned back pressure is adjusted using the pressure adjustmenting mechanism, thus structure
Become, keep above-mentioned swirling scroll 7 suitable to the extruding force of above-mentioned fixed eddy plate 8, improves the leakproofness of above-mentioned discharge chambe 11, and
Slippage loss can be reduced as much as possible.
Nearby the oily of space 29 is supplied via above-mentioned individual path 30 to above-mentioned back pressure chamber 28 above-mentioned crankshaft, which supplies extremely
The sliding parts such as the above-mentioned anti-rotation mechanism 10 in above-mentioned back pressure chamber 28.In addition, the oil also supply to above-mentioned swirling scroll 7 with it is above-mentioned
Sliding part, the sliding part of vortex 7b, 8b for being formed with above-mentioned discharge chambe 11 between fixed eddy plate 8 etc..It supplies to above-mentioned pressure
The oil of contracting room 11 spues from above-mentioned discharge opening 8d to above-mentioned discharge space 35, returns to the oil storage tank of above-mentioned 2 lower part of closed container
22。
Next, being illustrated using Fig. 1, Fig. 2 to the flowing of the oil in the present embodiment 1.
By oil supply mechanism portion 6, the oil of the oil storage tank 22 of 2 lower part of closed container is supplied to the oil supplying hole 12e in crankshaft 12,
Then, the space in convolution lug boss 7c is flowed to from the end of cam pin portion 12c.Then, oil flows to convolution bearing 7d, to it
It is lubricated, then flows into crankshaft space 29 nearby, a part of the oil is supplied via individual path 30 to back pressure chamber 28, above-mentioned
The remainder of oil is directed to than counterweight 21 by clearance portion 32 by lower part, via the oil extraction path 9d and row for being set to frame 9
Oil pipe 38 returns to above-mentioned oil storage tank 22.
As described above, in the present embodiment 1, the first seal member is set on the top of the ring portion 21a of counterweight 21
25, and thrust bearing 26 or such as Fig. 3 with the function as the second seal member are set as illustrated in fig. 2 in lower part
It is shown that thrust bearing 26 and the second seal member 31 are set.Thus, it is possible to prevent to the uneven portion 21b for being configured with counterweight 21
Space (back pressure chamber 28) in large quantities for oil supply, therefore, can be greatly reduced above-mentioned imbalance portion 21b to oil churn loss,
Realize that the performance of screw compressor improves.
In addition, in the present embodiment, more than the ring portion 21a internal side diameter of counterweight 21 is arranged at three abutted with crankshaft 12
Claw (support portion) 21c, and set the inner peripheral surface 21d of the above-mentioned ring portion 21a other than above-mentioned claw 21c to than crankshaft 12
Flange part 12d leans on radial outside.By inner peripheral surface 21d, above-mentioned claw 21c, above-mentioned crankshaft 12 and above-mentioned flange part 12d
Outer peripheral surface forms clearance portion 32, is connected to the top of above-mentioned counterweight 21 and the oily access of lower part to be formed.
Also consider in the flange part 12d setting through hole of crankshaft 12 as oily access, but in order to be arranged in flange part 12d
Through hole needs to increase the outer diameter of above-mentioned flange part 12d.In contrast, such as the present embodiment in this way, counterweight 21 inner peripheral surface side
Above-mentioned clearance portion 32 is formed, thereby, it is possible to not increase the outer diameter of above-mentioned flange part 12d, and via by above-mentioned 32 shape of clearance portion
At big oily access, so that supply to the lubricating oil of convolution bearing 7d is swimmingly flowed out to oil extraction path 9d.
In addition, in the present embodiment, the inner circumferential side of above-mentioned counterweight 21 is other than the inner peripheral surface of claw 21c, it is also necessary to be formed
The inner peripheral surface 21d of part other than claw 21c.But counterweight 21 is generally mostly to be manufactured by agglomerated material, there is no need to process pawl
Above-mentioned inner peripheral surface 21d other than portion, not will lead to cost increase, and be capable of forming big oily access (clearance portion 32).Therefore,
The such situation of big oily access is formed compared to the flange part 12d in crankshaft, and in the present embodiment, no need to increase flange part 12d, nothing
Therefore cost reduction need to be can be realized in the oily access that flange part 12d processes long hole, fan shape.
In addition, in the embodiment described above the example, remain claw 21c in the inner circumferential side of above-mentioned ring portion 21a and grooving is set, by
This forms above-mentioned clearance portion 32, but it is also possible to crankshaft 12 is substantially fixed in the inner circumferential side of above-mentioned ring portion 21a
Mode is constituted, and forms axial through hole in above-mentioned ring portion 21c, and above-mentioned clearance portion 32 is arranged.
In addition, above-mentioned clearance portion 32 and the rotation of crankshaft 12 rotate together with, however, it is preferred to be configured to, institute as shown in Figure 1, Figure 2
Show, when above-mentioned clearance portion 32 is not positioned at the phase of the underface of above-mentioned individual path 30, above-mentioned individual path 30 and above-mentioned back
Pressure chamber (space of 25 outside diameter of the first seal member) 28 is connected to.That is, with individual path 30 become most eccentric position when with
In the case that the mode that above-mentioned back pressure chamber 28 is connected to is constituted, as long as at least one by above-mentioned claw 21c is set to above-mentioned cam pin
The eccentric direction of portion 12c.By being made into such structure, in the shape that above-mentioned individual path 30 is connected to above-mentioned back pressure chamber 28
Under state, there is above-mentioned claw 21c in the underface of above-mentioned individual path 30, without clearance portion 32.With this configuration, exist
The part of above-mentioned claw 21c, oil are difficult to flow downwards, therefore, can more reliably carry out from above-mentioned individual path 30 upwards
State the fuel feeding of back pressure chamber 28.
In addition, for the width of above-mentioned claw 21c, preferably with during the connection of above-mentioned individual path 30, in this point
The lower section of branch path 30 determines the width of claw 21c with the mode of above-mentioned claw 21c.
For example, in the case where connection in 30 degree of rotation angle range in turning around, the width shape of above-mentioned claw 21c
It is more than the width as the angular range for being equivalent to 30 degree.
Moreover, as shown in Figure 4, Figure 5, preferably above-mentioned clearance portion 32 and above-mentioned imbalance portion 21b is set on not face each other
Position, that is, be set to relative to crankshaft 12 center each other not become point symmetry position.It with this configuration, can will be above-mentioned
At least one of claw 21c is set to therefore can across the position of above-mentioned 12 face of crankshaft relative to above-mentioned imbalance portion 21b
The centrifugal force of the uneven portion 21b effect to counterweight 21 is blocked with above-mentioned claw 21c.Therefore, it is able to suppress above-mentioned counterweight 21
Deformation, therefore, the fastening force for being able to suppress counterweight relative to crankshaft 12 reduce.
Embodiment 2
Using Fig. 6~Fig. 8, the embodiment 2 of screw compressor of the invention is illustrated.Fig. 6 is to indicate the present embodiment 2
Figure, be comparable to the figure of Fig. 2, Fig. 7 is that crankshaft shown in fig. 6 and the figure of counterweight, Fig. 8 are from the end side in cam pin portion
Crankshaft shown in fig. 6 and the figure of counterweight from thrust bearing side.In the explanation of the present embodiment 2, with the above embodiments 1
It is illustrated centered on different parts, for part same as Example 1, omits the description.
In the present embodiment 2, as shown in fig. 6, being accommodated with swirling scroll 7, anti-rotation mechanism 10, crankshaft 12 inside frame 9
Main shaft part 12a, cam pin portion 12c, flange part 12d, counterweight 21, the first seal member 25, thrust bearing 26, the second sealing
Part 31 etc..
The present embodiment 2 and the above embodiments 1 the difference lies in that as shown in Figure 6 to 8, above-mentioned counterweight 21 is from crankshaft
12 upper end insertion, and to be set to the flange part 12d that the step segment difference of the inner peripheral surface of the ring portion 21a of counterweight 12 is connected to crankshaft 12
Be fixed on above-mentioned flange part 12d with the state for being equipped with the opposite side in the side of thrust bearing 26.
In addition, the groove 21e in the upper surface for the ring portion 21a for being formed in above-mentioned counterweight 21 is equipped with the first seal member 25,
The sliding surface 7e on 25 one side of the first seal member and the convolution lower end lug boss 7c of swirling scroll 7 is slided, and will circle round whirlpool on one side
It is sealed between disk 7 and the ring portion 21a of counterweight.
In addition, in the same manner as in the above embodiment 1, the sliding in the above-mentioned lower end convolution lug boss 7c of above-mentioned swirling scroll 7
Face 7e is equipped with individual path 30, which is used for according to the circumnutation of swirling scroll 7 radially crosscutting above-mentioned the
One seal member 25, by the oil supply of the high pressure in space 29 near crankshaft to back pressure chamber 28.In the present embodiment 2, by according to above-mentioned
The circumnutation of swirling scroll 7 constitutes in space 29 near above-mentioned crankshaft with the intermittent slit being connected to of above-mentioned back pressure chamber 28 above-mentioned
Individual path 30.
Thrust bearing 26 is installed in the end face 9c of the frame 9 opposed with the lower end surface flange part 12d of above-mentioned crankshaft 12.On
Thrust bearing 26 is stated by supporting above-mentioned flange part 12d to support the axial load to the effect of above-mentioned crankshaft 12.Therefore, at this
In embodiment, the load for acting on the axial direction such as rotor magnetic attraction of crankshaft 12 does not act on above-mentioned counterweight 21.
In the outer side in setting position of the above-mentioned thrust bearing 26 of the ratio of the end face 9c of frame 9 part is formed fluted
21f is equipped with the second seal member 31 in groove 21f.Second seal member 31 and the ring portion 21a of above-mentioned counterweight 21 are slided,
And it will be sealed between above-mentioned ring portion 21a and the end face 9c of said frame 9.
As shown in Figure 7, Figure 8, the internal side diameter of the ring portion 21b of counterweight 21 be equipped with three at more than (in the example, at three) to
Radially inner side claw outstanding (support portion) 21c, above-mentioned counterweight 21 are fixed on the flange part 12d of crankshaft 12 by claw 21c.
The inner peripheral surface 21d of counterweight 21 other than above-mentioned claw 21c is formed as than above-mentioned flange part 12d by radial outside.
It is formed by the flange part 12d of above-mentioned crankshaft 12 and the claw 21c of above-mentioned counterweight 21 and inner peripheral surface 21d by above-mentioned counterweight
The clearance portion 32 that the interconnecting piece of 21 and above-mentioned flange part 12d penetrates through in the axial direction.The clearance portion 32 is in the same manner as in the above embodiment 1
It is functioned as the oil for supplying to convolution bearing 7d by flowing to the oily access of the oil extraction path side 9d.
It in the present embodiment 2, also in the same manner as in the above embodiment 1, is configured to, is not located in above-mentioned clearance portion 32 upper
When stating the phase of the underface of individual path 30, above-mentioned individual path 30 is connected to above-mentioned back pressure chamber 28.In addition, above-mentioned clearance portion
32 can be set to the not position of face each other with above-mentioned imbalance portion 21b, i.e., set on the center relative to crankshaft 12 each other not at
For the position of point symmetry.It is identical as the above embodiments 1 for other structures.
As the structure of the above embodiments 2, also in the same manner as the above embodiments 1, counterweight 21 ring portion 21a it is upper
Portion is equipped with the first seal member 25, is equipped with the second seal member 31 in lower part, thereby, it is possible to limit imbalance of the oil to counterweight 21
The movement of portion 21b.Thus, it is possible to reduce above-mentioned imbalance portion 21b therefore scroll compression can be realized to the churn loss of oil
The performance of machine improves.
In addition, in the present embodiment, in the same manner as in the above embodiment 1, being formed with above-mentioned in the inner peripheral surface side of counterweight 21
Therefore gap portion 32 not will increase the outer diameter of the flange part 12d of crankshaft 12, can be big via being formed by above-mentioned clearance portion 32
Oily access makes supply to the lubricating oil of convolution bearing 7d swimmingly flow out to oil extraction path 9d.
Moreover, above-mentioned counterweight 21 is mostly made by sintered part, it is therefore not necessary to carry out to the above-mentioned inner peripheral surface 21d other than claw
Processing, not will increase cost, and be capable of forming big oily access (clearance portion 32).
In addition, directly supporting the flange part 12d of crankshaft, therefore even if Xiang Qu by thrust bearing 26 according to the present embodiment 2
Run-off the straight when axis 12 installs counterweight 21, also being capable of vertical support crankshaft 12 always.Therefore, it is able to suppress and support crankshaft 12
Each bearing part contact, the reliability of compressor can be further increased.Moreover, by the structure for doing cost implementation 2,
The diameter of thrust bearing 26 can be reduced, therefore, from this point, also can be realized cost reduction.
As explained above ground, each embodiment of screw compressor according to the present invention, is made into such as flowering structure: in above-mentioned crankshaft
Have between outer peripheral surface and above-mentioned counterweight inner peripheral surface and penetrates through the clearance portion (oily access) of above-mentioned counterweight in the axial direction, is set to than above-mentioned
The first seal member and be set to than above-mentioned clearance portion that clearance portion is leaned between the above-mentioned counterweight and above-mentioned swirling scroll of outside diameter
The second seal member between the above-mentioned counterweight and said frame of outside diameter, therefore, available effect below.
That is, the more than half of oil by convolution bearing flows to lower section (base bearing side) via above-mentioned clearance portion (oily access), remain
Remaining oil stream is to the back pressure chamber in the uneven portion for being equipped with counterweight, and therefore, limitation is oily to the back pressure chamber for being equipped with above-mentioned imbalance portion
Supply.Thereby, it is possible to reduce above-mentioned imbalance portion outstanding radially therefore to can be realized whirlpool to the churn loss of oil
The performance for revolving compressor improves.
In addition, clearance portion is arranged in the inner circumferential side of counterweight in the not set oily access of flange part of crankshaft, as oily access,
Therefore, the path of above-mentioned flange part and the simplification of processing are realized, and can be easy to set up sufficiently in flange part periphery
The oily access of size.To which cost will not be improved, and can be improved the reliability of compressor.
In addition, including various modifications example the present invention is not limited to the above embodiments.In addition, the above embodiments be for
The example for illustrating the present invention with being readily appreciated that and explaining in detail is not limited to the whole structures that must have illustrated.
Symbol description
1-screw compressor, 2-closed containers, 3-compression mechanical parts, 4-driving portions, 5-rotation axle portions, 6-fuel feeding
Mechanism part, 7-swirling scrolls, 7a-platen, 7b-swirling scroll vortex, 7c-convolution bearing portion, 7d-convolution bearing,
7e-sliding surface, 8-fixed eddy plates, 8a-platen, 8b-fixed eddy plate vortex, 8c-suction inlet, 8d-discharge opening, 9-
Frame, 9a-fixed eddy plate fastening face, 9b-gimbal axis bearing portion, 9c-end face, 9d-oil extraction path, 9e, 9f-cross-drilled hole, 10-
Anti-rotation mechanism, 11-discharge chambes, 12-crankshafts, 12a-main shaft part, 12b-countershaft portion, 12c-cam pin portion, 12d-are convex
Edge, 12e-oil supplying hole (through hole), 13-base bearings, 14-stators, 15-rotors, 16-motor, 17-electric terminals,
18-sub-frames, 19-supplementary bearings, 20-supplementary bearing shells, 21-counterweights, 21a-ring portion, 21b-imbalance portion, 21c-pawl
Portion's (support portion), 21d-inner peripheral surface, 21e, 21f-groove, 22-oil storage tanks, 23-suction lines, 24-discharge pipes, 25-the
One seal member, 26-thrust bearings (the second seal member), 28-back pressure chambers (space of the outside diameter of the first seal member),
Space (space of the internal side diameter of the first seal member) near 29-crankshafts, 30-individual paths, the 31-the second seal member,
32-clearance portions (oily access), 33,34-bolts, 35-discharge spaces, 36-access, 37-motor room, 38-oil extractions
Pipe.
Claims (11)
1. a kind of screw compressor, has: having the crankshaft in the cam pin portion relative to axle center bias；Swirling scroll,
Platen has vortex and set on the opposite side of the vortex and convex via the convolution that engages of convolution bearing with above-mentioned cam pin portion
The portion of rising；Fixed eddy plate with the vortex that the vortex with the swirling scroll engages；On fixing the fixed eddy plate and storing
Swirling scroll is stated, and there is the frame for the base bearing for supporting above-mentioned crankshaft；For making the driving portion of above-mentioned crankshaft rotation；Accommodate this
A little closed containers；And in order to the oil storage tank that will be set in the closed container oil supply to above-mentioned cam pin portion end and
It is formed in the above-mentioned axial oil supplying hole of song,
Above-mentioned screw compressor is characterized in that having:
Counterweight is configured in the said frame below above-mentioned swirling scroll, and is fixed on above-mentioned crankshaft, and supports for generating
Disappear and acts on the centrifugal force in the direction of centrifugal force in above-mentioned cam pin portion and above-mentioned swirling scroll；
The clearance portion of above-mentioned counterweight is penetrated through in the axial direction；
Set on the first seal member than above-mentioned clearance portion between the above-mentioned counterweight and above-mentioned swirling scroll of outside diameter；And
Set on the second seal member than above-mentioned clearance portion between the above-mentioned counterweight and said frame of outside diameter.
2. screw compressor according to claim 1, which is characterized in that
Have and be set to than above-mentioned clearance portion between the above-mentioned counterweight and said frame of outside diameter, and supporting role is in above-mentioned song
The thrust bearing of the thrust of axis,
The thrust bearing is used as above-mentioned second seal member simultaneously.
3. screw compressor according to claim 2, which is characterized in that
Above-mentioned thrust bearing is made of resin bearing.
4. screw compressor according to claim 1, which is characterized in that
Have supporting role in the thrust bearing of the thrust of above-mentioned crankshaft,
The thrust bearing is set to the radially inner side of above-mentioned second seal member.
5. screw compressor according to claim 1, which is characterized in that
Above-mentioned crankshaft in above-mentioned cam pin subordinate portion is equipped with the diameter flange part bigger than the crankshaft, is carried out by the flange part
State the axial positioning of counterweight.
6. screw compressor according to claim 5, which is characterized in that
Have and be set between above-mentioned counterweight and said frame and supporting role is in the thrust bearing of the thrust of above-mentioned crankshaft,
Above-mentioned counterweight is positioned in the axial direction by being set to the face of the side equipped with above-mentioned thrust bearing of the flange part of above-mentioned crankshaft.
7. screw compressor according to claim 5, which is characterized in that
Have supporting role in the thrust bearing of the thrust of above-mentioned crankshaft,
The thrust bearing is set as supporting above-mentioned flange part,
It is above-mentioned to be fixed on above-mentioned flange part by outside diameter with the bearing surface focused on than above-mentioned thrust bearing.
8. screw compressor according to claim 1, which is characterized in that
Above-mentioned clearance portion is formed between above-mentioned crankshaft outer peripheral surface and above-mentioned counterweight inner peripheral surface,
It is above-mentioned that claw as the support portion relative to above-mentioned crankshaft is circumferentially at least provided at three with focusing on its inner circumferential side,
Via the claw, above-mentioned counterweight is fixed on above-mentioned crankshaft,
Above-mentioned clearance portion is set between above-mentioned claw.
9. screw compressor according to claim 8, which is characterized in that
Above-mentioned counterweight has imbalance portion outstanding radially, set on above-mentioned counterweight above-mentioned claw at least one relative to
The center of above-mentioned crankshaft is set to the opposite side in above-mentioned imbalance portion.
10. screw compressor according to claim 8, which is characterized in that
Individual path, the individual path structure are formed in the sliding surface of the above-mentioned convolution lug boss opposed with above-mentioned first seal member
Become, according to the circumnutation of swirling scroll, is intermittently connected to space and the outer diameter of the internal side diameter of above-mentioned first seal member
The space of side,
It supplies via the above-mentioned oil supplying hole for being formed in above-mentioned crankshaft to the oil of above-mentioned cam pin portion upper end and is lubricating above-mentioned rotary shaft
After holding, the sky for the outside diameter that a part of the oil is intermittently supplied via above-mentioned individual path to above-mentioned first seal member
Between.
11. screw compressor according to claim 10, which is characterized in that
By be arranged on the eccentric direction in above-mentioned cam pin portion above-mentioned claw at least one, be configured to, in above-mentioned clearance portion
When not positioned at the phase of the underface of above-mentioned individual path, the sky of the outside diameter of above-mentioned individual path and above-mentioned first seal member
Between be connected to.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016-149770 | 2016-07-29 | ||
| JP2016149770A JP6715722B2 (en) | 2016-07-29 | 2016-07-29 | Scroll compressor |
| PCT/JP2017/025717 WO2018021062A1 (en) | 2016-07-29 | 2017-07-14 | Scroll compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109642570A true CN109642570A (en) | 2019-04-16 |
| CN109642570B CN109642570B (en) | 2020-08-04 |
Family
ID=61016090
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201780040848.9A Active CN109642570B (en) | 2016-07-29 | 2017-07-14 | Scroll compressor having a plurality of scroll members |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6715722B2 (en) |
| CN (1) | CN109642570B (en) |
| WO (1) | WO2018021062A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2021203638A1 (en) * | 2020-04-07 | 2021-10-14 | 艾默生环境优化技术(苏州)有限公司 | Counterbalance assembly for scroll compressor, and scroll compressor |
| CN113944631A (en) * | 2020-07-17 | 2022-01-18 | 日立江森自控空调有限公司 | Scroll compressor and refrigeration cycle device |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7466063B2 (en) | 2021-07-02 | 2024-04-11 | 日立ジョンソンコントロールズ空調株式会社 | Scroll compressor and refrigeration cycle device |
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| JPS6170194A (en) * | 1984-09-12 | 1986-04-10 | Hitachi Ltd | Scroll fluid machine |
| JPH10159761A (en) * | 1996-11-28 | 1998-06-16 | Zexel Corp | Scroll compressor |
| DE10125357A1 (en) * | 2000-05-24 | 2001-12-06 | Toyoda Automatic Loom Works | Sealing structure in a scroll compressor |
| JP2005163687A (en) * | 2003-12-04 | 2005-06-23 | Hitachi Ltd | Electric compressor and its manufacturing method |
| CN201288666Y (en) * | 2008-09-19 | 2009-08-12 | 广州日立压缩机有限公司 | Structure for axial push stopping apparatus of cyclone compressor |
| JP2011190779A (en) * | 2010-03-16 | 2011-09-29 | Hitachi Appliances Inc | Scroll fluid machine |
| CN102235354A (en) * | 2010-04-23 | 2011-11-09 | 日立空调·家用电器株式会社 | Vortex compressor and refrigeration circulating device |
| JP2012017656A (en) * | 2010-07-06 | 2012-01-26 | Sanden Corp | Scroll compressor |
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|---|---|---|---|---|
| US4875838A (en) * | 1988-05-12 | 1989-10-24 | Tecumseh Products Company | Scroll compressor with orbiting scroll member biased by oil pressure |
| JP2000179481A (en) * | 1998-12-14 | 2000-06-27 | Hitachi Ltd | Scroll type compressor |
| JP2003176794A (en) * | 2002-12-13 | 2003-06-27 | Hitachi Ltd | Scroll compressor |
| JP6611468B2 (en) * | 2015-05-19 | 2019-11-27 | 日立ジョンソンコントロールズ空調株式会社 | Scroll compressor |
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2016
- 2016-07-29 JP JP2016149770A patent/JP6715722B2/en active Active
-
2017
- 2017-07-14 CN CN201780040848.9A patent/CN109642570B/en active Active
- 2017-07-14 WO PCT/JP2017/025717 patent/WO2018021062A1/en active Application Filing
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6170194A (en) * | 1984-09-12 | 1986-04-10 | Hitachi Ltd | Scroll fluid machine |
| JPH10159761A (en) * | 1996-11-28 | 1998-06-16 | Zexel Corp | Scroll compressor |
| DE10125357A1 (en) * | 2000-05-24 | 2001-12-06 | Toyoda Automatic Loom Works | Sealing structure in a scroll compressor |
| JP2005163687A (en) * | 2003-12-04 | 2005-06-23 | Hitachi Ltd | Electric compressor and its manufacturing method |
| CN201288666Y (en) * | 2008-09-19 | 2009-08-12 | 广州日立压缩机有限公司 | Structure for axial push stopping apparatus of cyclone compressor |
| JP2011190779A (en) * | 2010-03-16 | 2011-09-29 | Hitachi Appliances Inc | Scroll fluid machine |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2021203638A1 (en) * | 2020-04-07 | 2021-10-14 | 艾默生环境优化技术(苏州)有限公司 | Counterbalance assembly for scroll compressor, and scroll compressor |
| CN113944631A (en) * | 2020-07-17 | 2022-01-18 | 日立江森自控空调有限公司 | Scroll compressor and refrigeration cycle device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6715722B2 (en) | 2020-07-01 |
| WO2018021062A1 (en) | 2018-02-01 |
| JP2018017211A (en) | 2018-02-01 |
| CN109642570B (en) | 2020-08-04 |
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